Shaft locking device

ABSTRACT

The invention provides means for concentrically mounting a ring on a shaft and for automatically locking the same. Only one sleeve part is required, in addition to the ring. Reliance is placed on first coacting mated tapering surfaces on the sleeve and ring bore, to establish the concentric relation, and upon second coacting cam formations integral with the sleeve and ring, to establish axially cammed displacement of the ring and sleeve into locked concentric relation. In the forms disclosed, the sleeve is split and may have frictional interference with the mounting-shaft size, and the sleeve is held captive, in unithandling assembled relation within the ring bore. Also, in the forms disclosed, the ring is the inner race ring of an antifriction bearing, and the concentric tapering surfaces are positioned to directly radially and concentrically support the raceway region.

United States Patent 1 Howe, Jr.

[54] SHAFT LOCKING DEVICE Ralph S. Howe, Jr., New Britain, C010.

[73] Assignee: Textron Inc., Providence, R.l.

[22] Filed: April 19, 1971 [75] Inventor:

[21] App1.No.: 135,314

Primary ExaminerMilton Kaufman Assistant Examiner-Frank SuskoAtt0rneySandoe, l-lopgood & Calimafde 1 3,709,575 [4 1 Jan. 9, 1973 [57]ABSTRACT The invention provides means for concentrically mounting a ringon a shaft and for automaticallylocking the same. Only one sleeve partis required, in addition to the ring. Reliance is placed on firstcoacting mated tapering surfaces on the sleeve and ring bore, toestablish the concentric relation, and upon second coacting camformations integral with the sleeve and ring, to establish axiallycammed displacement of the ring and sleeve into locked concentricrelation. In the forms disclosed, the sleeve is split and may havefrictional interference with the mountingshaft size, and the sleeve isheld captive, in unit-handling assembled relation within the ring bore.Also, in the forms disclosed, the ring is the inner race ring of anantifriction bearing, and the concentric tapering surfaces arepositioned to directly radially and concentrically support the racewayregion.

19 Claims, 4 Drawing Figures PATENTEDJAN 9 1975 SHAFT LOCKING DEVICEThis invention relates to shaft-locking mechanism for locked mounting ofan article, such as an anti-friction bearing, on a shaft.

Aside from the age-old techniques employing one or more set-screws toanchor a hub or ring to a shaft, there have been various techniquesemploying a locking collar, with lock reaction between mating eccentricsurfaces on axially overlapped regions of the collar and hub or ring.Insofar as I am aware, all such techniques produce angularly localstress concentration, resulting not only in local ring deformation anddisplacement, but also in a degree of misalignment of the ring axis withrespect to the shaft axis. If the ring is part of an antifrictionbearing, these conditions spoil the truly concentric orientation of therace, to an extent which becomes intolerable for many applications. Theproblem of concentric mounting has been the subject of various measures,all of which are unduly complex, expensive or are otherwise inadequate,insofar as I am aware.

It is, accordingly, an object of the invention to provide an improvedshaft-locking structure, avoiding deficiencies of past structures.

Another object is to provide shaft-locking structure which is alsoinherently concentric in its action, supporting a hub, ring on the likeon a shaft.

A further object is to meet the above objects with mechanism which maybe pre-assembled with the hub or ring, and which is thus aself-retaining unit-handling shaft-lockable subassembly.

It is a specific object to achieve the foregoing objects with structurerequiring no more than one part, in addition to the hub or ring.

Another specific object is to provide structure of the characterindicated whereby a given inner bearing ring or the like may beeffectively locked to a selected one of a variety of shaft sizes.

It is a general object to provide locking mechanism of the characterindicated which is relatively simple and inexpensive, which may besubstantially blind in installed position, presenting no snaggingprojections or edges, and which may be inherently axially compact.

Other objects and various further features of novelty and invention willbe pointed out or will occur to those skilled in the art from a readingof the following specification in conjunction with the accompanyingdrawings. In said drawings, which show, for illustrative purposes only,preferred forms of the invention:

FIG. 1 is a vertical sectional view of an anti-friction bearingassembled in unit-handling relation with locking means of the invention;

FIG. 2 is an enlarged fragmentary sectional view of the parts in lockedrelation to a shaft, the section being taken for the condition ofrelative rotation of inner parts, away from the relation depicted inFIG. 1;

FIGS. 3 and 4 are views corresponding to FIGS. 1 and 2, respectively, toshow a modification.

Briefly stated, the invention provides means for concentrically mountinga ring on a shaft and for automatically locking the same. Only onesleeve part is required, in addition to the ring. Reliance is placed onfirst coacting mated tapering surfaces on the sleeve and ring bore, toestablish the concentric relation, and upon second coacting camformations integral with the sleeve and ring, to establish axiallycammed displacement of the ring and sleeve into the concentric relation.In the forms disclosed, the sleeve is split and preferably hasfrictional interference with the mounting-shaft size, and the sleeve isheld captive, in unit-handling assembled relation within the ring bore.

In FIGS. 1 and 2, the invention is shown in application to anantifriction bearing comprising inner and outer rings 10-11, withopposed circumferentially continuous raceways, 12-13, and with a set ofantifriction elements 14 riding both raceways and supporting the rings10-11 in spaced relation. A sleeve 15 is positioned in the bore of theinner ring 10. Sleeve 15 has an axially elongate cylindrical bore 16 forlocked mounting to a shaft 17, and it is the formation of sleeve 15 andits fit to and coaction with the bore of ring 10 which establish thelocked mounting of the invention.

The sleeve 15 possesses a degree of radially compliant action because itis preferred that its bore shall have resiliently loadedinterference-fit engagement with the shaft 17. Thus, sleeve 15 may be ofmolded plastic and circumferentially continuous, to serve certain loadranges. On the other hand, I indicate my present preference that sleeve15 be split, as at the angular locality indicated at 18; such a sleevemay be of relatively hard and incompressible material such as steel,powdered metal, or molded plastic (e.g., a relatively dense urethane),the desired compliant action being provided radially (i.e., radialexpansion or contraction of sleeve 15, with respect to its unstressedradial extent R in view of the split at 18.

For concentric support of the ring 10 and its raceway 12, elongatedgently tapered conical surfaces determine the fit, preferably over anaxially extensive region which conservatively spans the entirerace-supporting volume of ring 10, as at least between gage points20-21. As shown, the concave one of these tapers is identified 22, beingformed in a first axial region beneath raceway l2, and extendingcoaxially with the raceway 12, from an inlet cylindrical bore 23 ofnominal reduced radius R to a large end of radius R shown atintersection with an eccentric counterbore 24 in ring 10. The convex oneof these tapers is identified 25 and characterizes the substantial axiallength of sleeve 15, extending from a reduced end of radiussubstantially R, to a large end of radius R, which is preferablyslightly greater than R so that the end of sleeve 15 substantiallyoverhangs and spans the counterbore 24. As shown, the large end ofsleeve surface 25 terminates at a slightly inclined truncating edge 26,defined by intersection with an eccentric conical surface 27, whichcharacterizes the remaining exterior contour of sleeve 15.

In accordance with the invention, integral axially camming formations,reacting between sleeve 15 and ring 10 upon their relative rotation, arerelied upon to axially displace sleeve 15 and ring 10 to the point offirmly locked and coaxial reference of raceway 12 with respect to shaft17; in this situation, sleeve 15 is an annular wedge having large andsubstantially uniformly distributed axial and circumferential footing onshaft 17, and providing essentially the same kind of well-distributedsupport for ring 10, in the raceway body region 20-21. As shown,axial-camming action derives from reaction between the eccentric conicalsurface 27 and a similar but concave conical surface 28 in the counterbore 24. The surfaces 27-28 are relatively steeply tapered at an anglea, which is preferably substantially 45, or at least no less thansubstantially 40, so that a substantial axially reacting force componentdevelops from eccentric-surface engagement, as the sleeve 15 and ringare subjected to relative rotation. In FIG. 1, the legend E identifiesthe eccentric offset of both camming conical surfaces, with respect tothe sleeve axis common to surfaces 16-25 (in the case of surface 27),and with respect to the axis common to surfaces 12-22 (in the case ofsurface 28).

The remaining bore contour of ring 10 may be cylindrical at the adjacentend 29, and of the same nominal radius R, as that shown for the oppositeend 23. The end 29 may be of sufficient axial extent to permit formationof a drift-pin hole 30 or other local tool-engageable discontinuitytherein, for use in setting or releasing a locked condition. Whenpreassembled, as shown in FIG. 1 i.e., with sleeve in substantially itsunstressed condition, the range of overlap and sizing of conicalsurfaces 22-25 and 27-28 is preferably such that a small axial clearanceS exists, to allow an axial displacement S of sleeve 15 to the right (inthe sense of FIG. 1), thereby providing a degree of radial clearance forexpansion of sleeve 15 when pressed into slight interference-fitrelation with shaft 17.

It will be noted that in the FIG. 1 situation, wherein the notedeccentric axes are in or substantially in register, a measure of radialoverlap exists between sleeve 15 and the axially entrapping (and,therefore, retaining) reduced ends 23-29 of the bore of ring 10. It willbe understood that the radially compliant compressibility of sleeve 15should be such as to permit axial endwise inserting assembly of sleeve15 to the ring bore, i.e., past the region of transiently compressedyielding interference with one of the reduced ends 23-29 of the bore.Once past this constriction, sleeve 15 resiliently restores itself tothe size and positioning illustrated by FIG. 1. In the case of a splitsleeve 15, as shown, the effective angular extent of the split must besized to accommodate the temporary compliant constriction involved inthe pre-assembly step.

In practice, the pre-assembly of sleeve 15 to ring 10 may be amanufacturing step, in which case the complete antifriction bearingcarries and retains its own locking and mounting means, all packaged asa unit-handling article. Alternatively, the fully assembled bearing(10-11-14) may be packaged with one or more unassembled sleeves 15, allhaving the same, described external contour -27, but each having adifferent cylindrical bore radius R,,, to provide selectiveapplicability to a range of different shaft diameters. In every case,however, the sleeve 15, with bore radius R, selected for frictionalinterference-fit to the desired diameter of shaft 17, is pre-assembledto the bearing ring 10 prior to assembly to the shaft. Generally, it isdesired that shaft assembly proceed with shaft entry at the end 23, toassure maximum freedom for sleeve expansion (after closing the clearanceS); this is a simple manual operation, and the bearing is then displacedalong the shaft to its desired mounting location. The frictional grip ofsleeve 15- on shaft 17 is sufficient to temporarily hold a selectedposition, should it be necessary to position other elements beforelocking the position of bearing ring 10. All that is needed for lockingis to rotate ring 10 until jammed, with or without use of a tool at 30.Jamming results from axial-camming of the sleeve wedge 15 between shaft17 and bore portion 22, through the engagement of interfering rises ofthe eccentric surfaces 27-28 (see FIG. 2). In general, it is preferredthat dimensions and proportions be selected to achieve the jammed(locked) condition for a partial relative rotation of ring 10 and sleeve15 to the extent of 30 to from the condition depicted in FIG. 1.

It should be noted that for a unidirectionally rotated shaft 17 orbearing outer ring 11, there is a given correct direction of rotation inorder to establish a permanent locked condition of sleeve 15 to theshaft 17 and ring 10. Continued loaded rotation in the same directionimproves the locked condition, as long as there is a sufficient remnantlocal radial deformability of the sleeve 15 in its engagement to theshaft 17 or in its engagement to the bore portion 22, the action being aplanetary creep between two adjacent loaded surfaces of slightlydifferent radius. Eventually, however, all engaged coaxial surfaces willhave merged on coincident radii of local contact, the lock being tightlyand concentrically set when creep action ends. Should the workingrotation be in the opposite direction, in the presence of sufficientradial load, the initial setting of the lock will be released,momentarily, and then lock action will re-establish itself for theoppositely rotated direction of ring 10 with respect to sleeve 15,resulting in just as secure and just as concentric a support for theraceway 12. During the momentary release, the axial positioning of ring10 on shaft 17 is not lost, because of the inherent preloaded frictionalgrip which resulted from initial interference-fit assembly of sleeve 15to shaft 17.

FIGS. 3 and 4 illustrate a modification, wherein corresponding bearingand sleeve parts and the shaft are given the same reference numbers, butwith primed notation. The primary difference between the embodiments ofFIGS. 1 and 3 is that in FIG. 1, the gently tapered surfaces (22-25) andsteeply tapered surfaces (27-28) are converging in directions away froma radial plane between them, whereas in FIG. 3 the corresponding gentlytapered surfaces (22-25') and steeply tapered surfaces (27'-28) aredivergent in directions away from a radial plane between them. Thus, thesleeve 15' of FIGS. 3 and 4 has a cylindrical bore 16 of nominal radiusR,, and a gently tapered concentric outer conical surface 25 whichextends from a large outer end (of radius R.,), to a reduced or smallerend (of minimum radius R at juncture with the steeply inclined eccentricconical camming surface 27'. Surface 27' is one face of an enlarged andotherwise cylindrical end 31 of sleeve 15'; the cylindrical surface 31is eccentric about the same axis as is conical surface 27'. In similarfashion, the gently tapering elongated concave surface or bore portion22' (concentric with raceway 12') extends from a large end (of at leastthe radius R to a reduced end (of radius R,,, greater than R,) at ornear juncture with the steeply inclined eccentric conical surface 28'.Surface 28 flares outwardly to juncture with a cylindrical counterbore32, having a radius R, which clears the maximum eccentric extent of thesleeve end 31. To complete the profile shown, a short relieving conicalfillet 33 connects the primary conical surfaces 22'-28, fillet 33 beingconcentric with the bearing axis and serving to avoid stressconcentration along intersection of adjacent tapering surfaces.

As with FIG. 1, the sleeve 15 and inner ring have regions of radialoverlap serving to entrap or axially retain sleeve in pre-assembledrelation with ring 10'. And all axial end corners are preferablychamfered, as shown, The gap 18' at the split of sleeve 15 is of angularextent to permit transient radial compression of the lesser enddimension (compressed from the unstressed radius R to the lesser orthroat radius R,,, for right-to-left end-wise pre-assembling insertionof sleeve 15 in the bore of ring 10'. Once pre-assembled, the resilientnature of sleeve 15 returns the same to its unstressed condition, shownin FIG. 3. Assembly to the shaft 17' is as described for FIGS. 1 and 2,the direction of shaft insertion in sleeve 15 being preferablyrightto-left, in the sense of the drawings. Once in desired location,sleeve 15 has preloaded resilient grip to shaft 17', to hold the axiallocation, and the lock is set by rotation of ring 10' until jammed, bytool action at if desired. Axially directed cam action between surfaces27'-28 draws the annular wedge of sleeve 15 into circumferentially andaxially extensive intimate concentric engagement with shaft 17' and withthe bore portion 22, as shown in FIG. 4.

It will be seen that I have described improved and highly effectivelocking and mounting means meeting all stated objects. The action isaxially and circumferentially extensive, assuring concentric anddirectly radial support of the raceway 12 (12'), without danger of theangular misalignment or shaft-scoring, which characterize mounting withknown locking-collar devices. No set screws or threads are required,thus providing important economies. Further economies are realized byreason of the inherently simple machining operations which may be usedto generate all surfaces, and by adaptability to molding techniques asmay best accommodate the particular selected materials; for example, allmachined surfaces, including the eccentric surfaces, may be cut on astandard automatic multiplespindle screw machine.

It will be understood that cam angles, eccentricities, andconcentric-taper angles for frictional and other properties, may vary asdictated by particular requirements; generally speaking, the gentlytapered concentric conical angle B is at least no greater thansubstantially 10, being preferably of 2 to 5 slope with respect to thebearing axis. A given bearing can be accurately mounted upon and lockedto a relatively wide range of shaft diameters, through proper choice ofbore size for sleeve 15 (15). The assembly is inherently compact as toaxial-width requirements, lending itself to blind assembly of thesleeve, and with no snagging projections. Also, for the conventionalapplication in which the outer bearing ring 11 is first mounted in frameor housing structure (not shown), the preassembled -nature of thebearing assures that inner ring 10 (which must be partially rotated toachieve mounted and locked relation to the shaft) will always beconcentrically positioned and rotated, throughout the mounting andlocking procedure.

What is claimed is:

1. In combination, a bearing or the like ring having a bore and alocking element carried within the bore for locking said ring to ashaft; said ring having a first relatively gently tapered elongatedconical bore portion concentric with the ring axis and a relativelysteeply tapered conical counterbore at one end of said bore portion,said counterbore being eccentric to the ring axis, and said tapers beinginclined in opposite directions with respect to a radial plane betweensaid surfaces; said locking element comprising a split sleeve having acylindrical bore sized for fit with an intended mounting-shaft size,said sleeve having an outer contour characterized by a first gentlytapered elongated conical surface portion concentric with the sleevebore and in substantial coaxial registry with said first bore portion,said outer contour being further characterized by a second andrelatively steeply tapered surface portion in substantial registry withand facing said counterbore.

2. The combination of claim 1, in which the inclination of said tapersis such as to converge both tapers in directions away from said radialplane.

3. The combination of claim 1, in which the inclination of said tapersis such as to expand both tapers in directions away from said radialplane.

4. The combination of claim 1, in which said relatively gentle tapersare substantially the same and are at least no greater thansubstantially 10.

5. The combination of claim 4, in which said relatively gentle tapersare in the range of 2 to 5.

6. The combination of claim 1, in which said relatively steep tapers aresubstantially the same and are at least no less than substantially 40.

7. The combination of claim 6, in which said relatively steep tapers aresubstantially 45.

8. In combination, a bearing inner ring comprising having an outwardlyfacing circumferentially continuous antifriction-element raceway in afirst axial region, said ring having a bore characterized by arelatively gently tapered elongated conical bore portion coaxial withsaid raceway and in substantial overlap with said first axial region, asleeve having a cylindrical bore sized for fit with an intendedmounting-shaft size, said sleeve having an outer conical surfaceconcentric with said cylindrical bore and of substantially the sametaper as said gently tapered bore portion, said bore portion and outerconical surface having circumferential and axially extensiveinterference when overlapped in said first axial region, andaxially-operative cam means includingcoacting eccentric similarlytapered portions of said ring and sleeve in a second axial region oftheir overlap, said cam means being operative upon relative rotation ofsaid ring and sleeve to axially cam said ring and sleeve in thedirection to engage said gently tapered bore portion with said conicalsurface.

9. The combination of claim 8, in which'said first axial region is ofgreater axial extent than said raceway and fully overlaps the same,whereby antifriction element support is directly and uniformly radialwith respect to the ring axis.

10. The combination of claim 8, in which said second axial region isaxially offset from said first axial region, where any asymmetry ofaxial camming force development is substantially local to a regionremoved from that of antifriction-element support.

11. The combination of claim 8, in which said sleeve is characterized bya degree of radially compliant expandable action.

12. The combination of claim 11, in which said sleeve is of metal. I

13. The combination of claim 11, in which said sleeve is of plasticmaterial.

14. in combination, a bearing inner ring comprising having an outwardlyfacing circumferentially continuous antifriction-element raceway in afirst axial region, said ring having a bore characterized by arelatively gently tapered elongated conical bore portion coaxial withsaid raceway and in substantial overlap with said first axial region, asleeve having a cylindrical bore sized for fit with an intendedmounting-shaft size, said sleeve having an outer conical surfaceconcentric with said cylindrical bore and of substantially the sametaper as said gently tapered bore portion, said bore portion and outerconical surface having circumferential and axially extensiveinterference when overlapped in said first axial region, andaxially-operative cam means including coacting portions of said ring andsleeve in a second axial region of their overlap, said cam meanscomprising relatively steeply inclined eccentric tapered surfaces onsaid ring and sleeve and being operative upon relative rotation of saidring and sleeve to axially cam said ring and sleeve in the direction toengage said gently tapered bore portion with said conical surface.

15. The combination of claim 14, in which said sleeve is split.

16. The combination of claim 14, in which the tapering directions ofsaid relatively gentle taper and of said relative steep taper areaxially opposed, both tapers of said ring having a region of radialoverlap with both tapers of said sleeve, whereby axial retention of anassembled ring and sleeve is inherent, said sleeve being split andstiffly compliantly deformable, the angular extent of the split beingsuch in relation to the extent of said region of radial overlap for atleast one axial direction of inserted assembly of said sleeve into saidring that said sleeve may be transiently radially compressed to permitsuch assembly.

shaft, with interference-fit frictional engagement of said sleeve to theshaft, and then the ring is rotated to establish eccentrically cammedlocking of the raceway in concentric relation to the shaft, withoptional provision for tool-applied torque to set the lock.

18. In combination, a bearing inner ring comprising having an outwardlyfacing circumferentially continuous antifriction-element raceway in afirst axial region, said ring having a bore characterized by arelatively gently tapered elongated conical bore portion coaxial withsaid raceway and in substantial overlap with said first axial region, asleeve having a cylindrical bore sized for fit with an intendedmounting-shaft size, said sleeve having an outer conical surfaceconcentric with said cylindrical bore and of substantially the sametaper as said gently tapered bore portion, said bore portion and outerconical surface having circumferential and axially extensiveinterference when overlapped in said first axial region, andaxially-operative cam means including'coacting portions of said ring andsleeve in a second axialregion of their overlap, said cam means beingoperative upon relative rotation of said ring and clamping action inaxially offset elation to said first axial region.

1. In combination, a bearing or the like ring having a bore and alocking element carried within the bore for locking said ring to ashaft; said ring having a first relatively gently tapered elongatedconical bore portion concentric with the ring axis and a relativelysteeply tapered conical counterbore at one end of said bore portion,said counterbore being eccentric to the ring axis, and said tapers beinginclined in opposite directions with respect to a radial plane betweensaid surfaces; said locking element comprising a split sleeve having acylindrical bore sized for fit with an intended mounting-shaft size,said sleeve having an outer contour characterized by a first gentlytapered elongated conical surface portion concentric with the sleevebore and in substantial coaxial registry with said first bore portion,said outer contour being further characterized by a second andrelatively steeply tapered surface portion in substantial registry withand facing said counterbore.
 2. The combination of claim 1, in which theinclination of said tapers is such as to converge both tapers indirections away from said radial plane.
 3. The combination of claim 1,in which the inclination of said tapers is such aS to expand both tapersin directions away from said radial plane.
 4. The combination of claim1, in which said relatively gentle tapers are substantially the same andare at least no greater than substantially 10*.
 5. The combination ofclaim 4, in which said relatively gentle tapers are in the range of 2*to 5*.
 6. The combination of claim 1, in which said relatively steeptapers are substantially the same and are at least no less thansubstantially 40*.
 7. The combination of claim 6, in which saidrelatively steep tapers are substantially 45*.
 8. In combination, abearing inner ring comprising having an outwardly facingcircumferentially continuous antifriction-element raceway in a firstaxial region, said ring having a bore characterized by a relativelygently tapered elongated conical bore portion coaxial with said racewayand in substantial overlap with said first axial region, a sleeve havinga cylindrical bore sized for fit with an intended mounting-shaft size,said sleeve having an outer conical surface concentric with saidcylindrical bore and of substantially the same taper as said gentlytapered bore portion, said bore portion and outer conical surface havingcircumferential and axially extensive interference when overlapped insaid first axial region, and axially-operative cam means includingcoacting eccentric similarly tapered portions of said ring and sleeve ina second axial region of their overlap, said cam means being operativeupon relative rotation of said ring and sleeve to axially cam said ringand sleeve in the direction to engage said gently tapered bore portionwith said conical surface.
 9. The combination of claim 8, in which saidfirst axial region is of greater axial extent than said raceway andfully overlaps the same, whereby antifriction element support isdirectly and uniformly radial with respect to the ring axis.
 10. Thecombination of claim 8, in which said second axial region is axiallyoffset from said first axial region, where any asymmetry of axialcamming force development is substantially local to a region removedfrom that of antifriction-element support.
 11. The combination of claim8, in which said sleeve is characterized by a degree of radiallycompliant expandable action.
 12. The combination of claim 11, in whichsaid sleeve is of metal.
 13. The combination of claim 11, in which saidsleeve is of plastic material.
 14. In combination, a bearing inner ringcomprising having an outwardly facing circumferentially continuousantifriction-element raceway in a first axial region, said ring having abore characterized by a relatively gently tapered elongated conical boreportion coaxial with said raceway and in substantial overlap with saidfirst axial region, a sleeve having a cylindrical bore sized for fitwith an intended mounting-shaft size, said sleeve having an outerconical surface concentric with said cylindrical bore and ofsubstantially the same taper as said gently tapered bore portion, saidbore portion and outer conical surface having circumferential andaxially extensive interference when overlapped in said first axialregion, and axially-operative cam means including coacting portions ofsaid ring and sleeve in a second axial region of their overlap, said cammeans comprising relatively steeply inclined eccentric tapered surfaceson said ring and sleeve and being operative upon relative rotation ofsaid ring and sleeve to axially cam said ring and sleeve in thedirection to engage said gently tapered bore portion with said conicalsurface.
 15. The combination of claim 14, in which said sleeve is split.16. The combination of claim 14, in which the tapering directions ofsaid relatively gentle taper and of said relative steep taper areaxially opposed, both tapers of said ring having a region of radialoverlap with both tapers of said sleeve, whereby axial retention of anassembled ring and sleeve is inherent, said sleeve being split andstiffly compliantly deformable, the angular extent of the split beingsuch in relation to the extent of said region of radial overlap for atleast one axial direction of inserted assembly of said sleeve into saidring that said sleeve may be transiently radially compressed to permitsuch assembly.
 17. The combination of claim 16, in which said ringincludes an externally accessible tool-engaging discontinuity for torqueapplication to said ring; whereby to install said combination on a shaftof said size, the assembly is first axially applied to desired positionon the shaft, with interference-fit frictional engagement of said sleeveto the shaft, and then the ring is rotated to establish eccentricallycammed locking of the raceway in concentric relation to the shaft, withoptional provision for tool-applied torque to set the lock.
 18. Incombination, a bearing inner ring comprising having an outwardly facingcircumferentially continuous antifriction-element raceway in a firstaxial region, said ring having a bore characterized by a relativelygently tapered elongated conical bore portion coaxial with said racewayand in substantial overlap with said first axial region, a sleeve havinga cylindrical bore sized for fit with an intended mounting-shaft size,said sleeve having an outer conical surface concentric with saidcylindrical bore and of substantially the same taper as said gentlytapered bore portion, said bore portion and outer conical surface havingcircumferential and axially extensive interference when overlapped insaid first axial region, and axially-operative cam means includingcoacting portions of said ring and sleeve in a second axial region oftheir overlap, said cam means being operative upon relative rotation ofsaid ring and sleeve to axially cam said ring and sleeve in thedirection to engage said gently tapered bore portion with said conicalsurface, said sleeve and ring having integral circumferentiallyextending and radially overlapping portions which axially retainassembly of said sleeve and ring, in readiness for shaft mounting. 19.The combination of claim 8, wherein said similarly tapered eccentricportions are sufficiently steep to develop both a substantialaxial-displacement force reaction and a substantial radially-compressiveclamping action in axially offset elation to said first axial region.